WO2004038224A1 - Variable-delivery rotary vane pump - Google Patents

Variable-delivery rotary vane pump Download PDF

Info

Publication number
WO2004038224A1
WO2004038224A1 PCT/IT2003/000658 IT0300658W WO2004038224A1 WO 2004038224 A1 WO2004038224 A1 WO 2004038224A1 IT 0300658 W IT0300658 W IT 0300658W WO 2004038224 A1 WO2004038224 A1 WO 2004038224A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
rotating ring
outer rotating
rotary pump
pump
Prior art date
Application number
PCT/IT2003/000658
Other languages
French (fr)
Inventor
Luca Marano
Giacomo Armenio
Original Assignee
Pierburg S.P.A.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg S.P.A. filed Critical Pierburg S.P.A.
Priority to AU2003283809A priority Critical patent/AU2003283809A1/en
Priority to EP03775790A priority patent/EP1579117A1/en
Publication of WO2004038224A1 publication Critical patent/WO2004038224A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/348—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the vanes positively engaging, with circumferential play, an outer rotatable member

Definitions

  • the present invention relates to a variable-delivery rotary vane pump, particularly for oil, and which may be used to advantage in automotive applications.
  • the present invention relates to a rotary vane pump of the type comprising a casing; and a rotation unit, in turn comprising an inner rotor and an outer rotating ring, between which are interposed a number of vanes .
  • this type of rotary pump is halfway between a gear pump and a vane pump.
  • a gear pump substantially comprises two rotating elements, one rotated by the other by means of teeth, which action produces, on the fluid between two meshing teeth, suction on one side of the centreline of the meshing arc, and thrust on the other side.
  • a vane pump provides for variable delivery, between zero and a maximum value, by varying the eccentricity of the two rotating elements.
  • German Patent DE-C1-195 32 703 describes a particular vane design for transmitting motion from the inner rotor to the outer rotating ring of a rotary pump; and each vane comprises a substantially round-section first portion which fits inside a respective seat formed in the outer ring, and a second portion shaped to fit inside a respective cavity on the rotor .
  • the inner rotor and outer rotating ring only have the same speed for a particular eccentricity value, and hence for a particular oil flow, which, as is known, varies in proportion to eccentricity.
  • variable-delivery rotary vane pump as claimed in Claim 1.
  • Figure 1 shows a diagram of the mechanics of a rotary pump in accordance with the present invention
  • Figure 2 shows an overall diagram (in the direction of arrow. ,V---in - Figure 4 ⁇ ) * **Of- the - Figure 1 pump ifor a first' eccentricity value;
  • Figure 3 shows an overall diagram (in the direction of arrow V in Figure 4) of the Figure 1 pump for a second, in particular zero, eccentricity value;
  • Figure 4 shows section along line A-A of the overall diagrams in Figures 2 and 3 ;
  • FIG. 5 shows the same section as in Figure 4.
  • Figure 6 shows a section along line B-B of the Figure 5 pump
  • Figure 7 shows a section along line C-C of the Figure 5 pump
  • FIG 8 shows the same section as in Figures 4 and 5;
  • Figure 9 shows a section along line D-D of the Figure 8 pump
  • Figure 10 shows a section along line E-E of the Figure 8 pump,-
  • Figures 11(A) and 11(B) show a first detail of the rotary pump according to the present invention
  • Figures 12 (A) and 12 (B) show a second detail of the rotary pump according to the present invention
  • Figures 13 (A) and 13 (B) show a third detail of the rotary pump according to the present invention
  • Figures 14 (A) and 14 (B) show a fourth detail of the rotary pump according to the present invention
  • Figures 15(A) and 15(B) show a fifth detail of the rotary pump according to the present invention.
  • pump 10 comprises a casing 11 housing the components described below.
  • casing 10 houses a gear 12 rotated, in the direction of arrow Rl and by a shaft (not shown) , about an axis X perpendicular to the drawing plane.
  • Gear 12 has a number of teeth 13 which mesh simultaneously with the teeth 14 of a rotor 15 rotating about an axis Y parallel to axis X, and with the teeth 16 of an outer rotating ring 17 rotating about an axis Z which, for a zero eccentricity value, coincides with axis Y (see below, with reference to Figure 3) .
  • Rotor 15 and outer rotating ring 17 form part of a rotating unit RU.
  • gear 12 meshes simultaneously with a portion of rotor 15 and a portion of outer rotating ring 17 by virtue of teeth 14 and 16 being aligned along axes Y and Z, and by virtue of containing the overall " dimensions of outer rotating ring
  • Rotor 15 and outer rotating ring 17 are rotated by gear 12 about respective axes Y and Z in the direction of arrow R2, opposite the direction of arrow Rl ( Figure 2) .
  • the outer surface 15a of rotor 15 and the inner surface 17a of outer rotating ring 17 define, in conventional manner, a pumping gap 18 divided into five pumping pockets 19 by five vanes 20 also forming part of rotating unit RU.
  • Each vane 20 comprises, in known manner, a first head 20a hinged inside a- respective seat 21 formed on outer rotating ring 17; and a second head 20b free to slide in a respective seat 22 formed on rotor 15.
  • outer rotating ring 17 have the same angular speed at any instant within each turn. In general, therefore, there is never any time in which outer rotating ring 17 accelerates or decelerates with respect to rotor 15.
  • the vanes provide for transmitting motion from the rotor to the outer ring, and must also support both the force required to pump the fluid and the inertial loads caused by acceleration and deceleration of the ring, whereas, in the present invention, the vanes have none of these functions, and can therefore be made, for example, of plastic material.
  • vanes to transmit motion not only complicates design, but results in irregular operation of the pump as a whole, due to the indefinite nature of the mechanics involved.
  • FIG. 15 One example of the vane 20 employed in the present invention is shown in Figure 15.
  • Eccentricity E (Figure 2) may be varied as required using a plate 23, as shown in detail in Figure 14.
  • Plate 23 comprises a substantially round first opening 24, inside which a portion 12a of gear 12 is inserted ( Figures 4, 12) and is free to rotate in the direction of arrow Rl .
  • Plate 23 also has a substantially round second opening 25 for housing a portion 17a of outer rotating ring 17 ( Figures 4, 11) .
  • the fit between the surface of portion 17a and second opening 25 is such as to allow outer rotating ring 17 to rotate freely in the direction of arrow R2.
  • plate 23 also comprises a relief opening 26 for the oil which would otherwise also be pumped as teeth 13 of gear 12 mesh with teeth 14 and 16 of rotor 15 and outer rotating ring 17 respectively.
  • pump 10 is fully immersed in the oil, and such pumping action - undesired in this case, but which, in an embodiment not shown, could constitute a successive oil pumping stage - would result in oil splash inside casing 11, thus resulting in loss of power.
  • plate 23 ( Figure 14) comprises a projection 27 projecting with respect to the main body of the plate.
  • projection 27 is acted on by a regulating device RD comprising, in known manner, an actuating member 28, which acts on a surface 27a of projection 27, while a surface 27b of projection 27, opposite surface 27a, is acted on by a spring 29.
  • Actuating member 28 and spring 29 are both housed inside a portion 11a of casing 11.
  • Actuating member 28 may be controlled by one of various known systems employed, in particular, in automotive applications.
  • actuator 28 is advantageously controlled by an electronic central control unit (not shown) , which determines other operating parameters of the internal combustion engine (not shown) with which pump 10 is associated.
  • oil from a tank flows through an inlet 30 ( Figure 4) into pockets 19 and then to an outlet 31, from which it is fed to at least one user device (not shown) .
  • oil flow can be varied by applying force F, which can be regulated in known manner .
  • force F which can be regulated in known manner .
  • the mechanics of the system can be represented as shown in Figure 1.
  • the mechanics of the system may be represented in the form of an epicyclic gear train, where the sun gear is defined by gear 12, the planet wheel by outer rotating ring 17, and the planet carrier simply by plate 23.
  • planet carrier 23 To achieve eccentricity E, planet carrier 23 must rotate by an angle ⁇ to produce a relative rotation ⁇ between rotor 15 and outer rotating ring 17.
  • vanes 20 may be made of materials of less than superior mechanical properties, e.g. plastic, etc.
  • materials of less than superior mechanical properties e.g. plastic, etc.
  • changes may be made to the rotary pump as described and illustrated herein without, however, departing from the scope of the present invention.
  • the first member of pump 10 to be rotated is rotor 15 directly, as opposed to gear 12.
  • gear 12 obviously serves to make the angular speeds of rotor 15 and outer rotating J ring 17 equal.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

A variable-delivery rotary pump (10) with oscillating vanes (20), having devices (12, 13, 14, 16) for simultaneously rotating the rotor (15) and the outer rotating ring (17) at the same rotation speed.

Description

VARIABLE-DELIVERY ROTARY VANE PUMP
TECHNICAL FIELD The present invention relates to a variable-delivery rotary vane pump, particularly for oil, and which may be used to advantage in automotive applications.
More specifically, the present invention relates to a rotary vane pump of the type comprising a casing; and a rotation unit, in turn comprising an inner rotor and an outer rotating ring, between which are interposed a number of vanes .
BACKGROUND ART
In a way, this type of rotary pump is halfway between a gear pump and a vane pump.
That is, like a gear pump, it substantially comprises two rotating elements, one rotated by the other by means of teeth, which action produces, on the fluid between two meshing teeth, suction on one side of the centreline of the meshing arc, and thrust on the other side.
A vane pump, on the other hand, as is known, provides for variable delivery, between zero and a maximum value, by varying the eccentricity of the two rotating elements.
German Patent DE-C1-195 32 703, for example, describes a particular vane design for transmitting motion from the inner rotor to the outer rotating ring of a rotary pump; and each vane comprises a substantially round-section first portion which fits inside a respective seat formed in the outer ring, and a second portion shaped to fit inside a respective cavity on the rotor .
In the embodiment illustrated in the above patent, however, the inner rotor and outer rotating ring only have the same speed for a particular eccentricity value, and hence for a particular oil flow, which, as is known, varies in proportion to eccentricity.
For the rotation speeds of the outer rotating ring and inner"-*rotor to
Figure imgf000003_0001
perfectly, in fact,' the vane profile should change for each eccentricity value, which is obviously impossible. Consequently, when the eccentricity of the pump is varied to vary delivery, the outer ring accelerates and decelerates in the course of each complete turn, though still maintaining a constant average angular speed, thus resulting in malfunctioning of the pump. DISCLOSURE OF INVENTION
It is an object of the present invention to provide a variable-delivery rotary vane pump designed to eliminate „the aforementioned 'drawbacks, and wherein the angular speeds of the inner rotor and outer rotating ring are always equal, at any instant within each complete turn.
According to the present invention, there is provided a variable-delivery rotary vane pump as claimed in Claim 1.
BRIEF DESCRIPTION OF THE DRAWINGS
A non-limiting embodiment of the present invention will be described by way of example with reference to the accompanying drawings, in which:
Figure 1 shows a diagram of the mechanics of a rotary pump in accordance with the present invention;
Figure 2 shows an overall diagram (in the direction of arrow. ,V---in -Figure 4~)***Of- the -Figure 1 pump ifor a first' eccentricity value;
Figure 3 shows an overall diagram (in the direction of arrow V in Figure 4) of the Figure 1 pump for a second, in particular zero, eccentricity value;
Figure 4 shows section along line A-A of the overall diagrams in Figures 2 and 3 ;
Figure 5 shows the same section as in Figure 4;
Figure 6 shows a section along line B-B of the Figure 5 pump;
Figure 7 shows a section along line C-C of the Figure 5 pump;
Figure 8 shows the same section as in Figures 4 and 5;
Figure 9 shows a section along line D-D of the Figure 8 pump;
Figure 10 shows a section along line E-E of the Figure 8 pump,-
Figures 11(A) and 11(B) show a first detail of the rotary pump according to the present invention;
Figures 12 (A) and 12 (B) show a second detail of the rotary pump according to the present invention;
Figures 13 (A) and 13 (B) show a third detail of the rotary pump according to the present invention; Figures 14 (A) and 14 (B) show a fourth detail of the rotary pump according to the present invention;
Figures 15(A) and 15(B) show a fifth detail of the rotary pump according to the present invention;
BEST MODE FOR CARRYING OUT THE INVENTION Number 10 in the accompanying drawings indicates a variable-delivery rotary vane pump in accordance with the present invention.
To begin with, pump 10 comprises a casing 11 housing the components described below. As shown in detail in Figures 2 to 4, casing 10 houses a gear 12 rotated, in the direction of arrow Rl and by a shaft (not shown) , about an axis X perpendicular to the drawing plane.
Gear 12 has a number of teeth 13 which mesh simultaneously with the teeth 14 of a rotor 15 rotating about an axis Y parallel to axis X, and with the teeth 16 of an outer rotating ring 17 rotating about an axis Z which, for a zero eccentricity value, coincides with axis Y (see below, with reference to Figure 3) .
Rotor 15 and outer rotating ring 17 form part of a rotating unit RU.
As shown particularly in Figure 4, gear 12 meshes simultaneously with a portion of rotor 15 and a portion of outer rotating ring 17 by virtue of teeth 14 and 16 being aligned along axes Y and Z, and by virtue of containing the overall "dimensions of outer rotating ring
17 in the direction of axes Y and Z. Rotor 15 and outer rotating ring 17 are rotated by gear 12 about respective axes Y and Z in the direction of arrow R2, opposite the direction of arrow Rl (Figure 2) .
The outer surface 15a of rotor 15 and the inner surface 17a of outer rotating ring 17 define, in conventional manner, a pumping gap 18 divided into five pumping pockets 19 by five vanes 20 also forming part of rotating unit RU.
Each vane 20 comprises, in known manner, a first head 20a hinged inside a- respective seat 21 formed on outer rotating ring 17; and a second head 20b free to slide in a respective seat 22 formed on rotor 15.
With particular reference to Figure 4, since at least one portion of rotor 15 and at least one portion of outer rotating ring 17 forming part of rotating unit RU have the same outside diameter D (Figure 4) and the same number of teeth 14, 16, rotor 15 and outer rotating ring
17 have the same angular speed at any instant within each turn. In general, therefore, there is never any time in which outer rotating ring 17 accelerates or decelerates with respect to rotor 15.
This is only true, however, when eccentricity E is fixed. In fact, as eccentricity E varies (see below) , outer ring 17 must rotate by a given angle (see below) , and so accelerates or decelerates. In no case, however, do the inertial loads pass through vanes 20.
Outer rotating ring 17, gear 12, and rotor 15 are shown in more detail in Figures 11, 12, 13.
In said Patent DE-C1-195 32 703, the vanes provide for transmitting motion from the rotor to the outer ring, and must also support both the force required to pump the fluid and the inertial loads caused by acceleration and deceleration of the ring, whereas, in the present invention, the vanes have none of these functions, and can therefore be made, for example, of plastic material.
Moreover, using the vanes to transmit motion not only complicates design, but results in irregular operation of the pump as a whole, due to the indefinite nature of the mechanics involved.
One example of the vane 20 employed in the present invention is shown in Figure 15.
Eccentricity E (Figure 2) may be varied as required using a plate 23, as shown in detail in Figure 14.
Plate 23 comprises a substantially round first opening 24, inside which a portion 12a of gear 12 is inserted (Figures 4, 12) and is free to rotate in the direction of arrow Rl .
Plate 23 also has a substantially round second opening 25 for housing a portion 17a of outer rotating ring 17 (Figures 4, 11) . The fit between the surface of portion 17a and second opening 25 is such as to allow outer rotating ring 17 to rotate freely in the direction of arrow R2.
As shown with particular reference to Figures 4 and
14, plate 23 also comprises a relief opening 26 for the oil which would otherwise also be pumped as teeth 13 of gear 12 mesh with teeth 14 and 16 of rotor 15 and outer rotating ring 17 respectively.
In this connection, it should be recalled that pump 10 is fully immersed in the oil, and such pumping action - undesired in this case, but which, in an embodiment not shown, could constitute a successive oil pumping stage - would result in oil splash inside casing 11, thus resulting in loss of power.
Finally, plate 23 (Figure 14) comprises a projection 27 projecting with respect to the main body of the plate. As shown in Figures 2 and 3, projection 27 is acted on by a regulating device RD comprising, in known manner, an actuating member 28, which acts on a surface 27a of projection 27, while a surface 27b of projection 27, opposite surface 27a, is acted on by a spring 29. Actuating member 28 and spring 29 are both housed inside a portion 11a of casing 11.
Actuating member 28 may be controlled by one of various known systems employed, in particular, in automotive applications.
The position of actuator 28 is advantageously controlled by an electronic central control unit (not shown) , which determines other operating parameters of the internal combustion engine (not shown) with which pump 10 is associated.
As can be seen, when actuating member 28 (controlled by means 'not shown) exerts "a force F on projection 27 of plate 23, plate 23 is rotated about axis X to switch, for example, from the Figure 2 configuration, in which eccentricity E is other than zero, to the Figure 3 configuration, in which eccentricity E equals zero.
In the first case (E other than zero) , in accordance with known principles in the construction of pumps of this sort, the oil is pumped, whereas, in the second (E equal to zero) , no pumping action is performed (zero delivery) .
In actual use, the oil from a tank (not shown) flows through an inlet 30 (Figure 4) into pockets 19 and then to an outlet 31, from which it is fed to at least one user device (not shown) . As stated, oil flow can be varied by applying force F, which can be regulated in known manner . The mechanics of the system can be represented as shown in Figure 1.
That is, the mechanics of the system may be represented in the form of an epicyclic gear train, where the sun gear is defined by gear 12, the planet wheel by outer rotating ring 17, and the planet carrier simply by plate 23.
To achieve eccentricity E, planet carrier 23 must rotate by an angle α to produce a relative rotation β between rotor 15 and outer rotating ring 17.
Moreover, being subjected to no inertial forces directly, vanes 20 may be made of materials of less than superior mechanical properties, e.g. plastic, etc. Clearly, changes may be made to the rotary pump as described and illustrated herein without, however, departing from the scope of the present invention.
For example, in a variation not shown, the first member of pump 10 to be rotated is rotor 15 directly, as opposed to gear 12. In this case, too, gear 12 obviously serves to make the angular speeds of rotor 15 and outer rotating Jring 17 equal.'

Claims

1) A variable-delivery rotary pump (10) with oscillating vanes (20) , of the type comprising a casing (11) , and a rotation unit (RU) in turn comprising a rotor (15) and an outer rotating ring (17) , between which are interposed a number of said oscillating vanes (20) defining a corresponding number of pumping pockets (19) ; a first end portion (20a) of each of said oscillating vanes (20) being fitted inside a respective seat (21) formed on said rotor (15) ; and a second end portion (20b) of each of said oscillating vanes (20) being hinged inside a respective seat (22)' formed on said outer rotating ring (17), so that each oscillating vane (20) rotates about a hinge axis; the variable-delivery rotary pump (10) being characterized by comprising means (12, 13, 14, 16) for simultaneously rotating said rotor (15) and said outer rotating ring (17) at the same rotation speed.
2) A rotary pump (10) as claimed in Claim 1, wherein said means (12, 13, 14, 16) comprise a gear (12) meshing simultaneously with said rotor (15) and said outer rotating ring (17) ; at least one portion of said rotor (15) and at least one portion of said outer rotating ring (17) having the same diameter (D) and an equal number of teeth (14, 16) .
3) A rotary pump (10) as claimed in Claim 2, wherein the eccentricity (E) between the centre of said outer rotating ring (17) and the centre of said rotor (15) is varied by means of an oscillating plate (23) acted on by actuating means (28) . 4) A rotary pump (10) as claimed in Claim 3, wherein said oscillating plate (23) comprises oil relief means (26) .
5) A rotary pump (10) as claimed in any one of the foregoing Claims, wherein said oscillating vanes (20) are made of plastic material.
6) A rotary pump (10) as claimed in Claim 3, wherein an electronic central control unit is provided to regulate the position of said actuating means (28) .
PCT/IT2003/000658 2002-10-23 2003-10-23 Variable-delivery rotary vane pump WO2004038224A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2003283809A AU2003283809A1 (en) 2002-10-23 2003-10-23 Variable-delivery rotary vane pump
EP03775790A EP1579117A1 (en) 2002-10-23 2003-10-23 Variable-delivery rotary vane pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBO2002A000668 2002-10-23
IT000668A ITBO20020668A1 (en) 2002-10-23 2002-10-23 VARIABLE FLOW ROTARY VANE PUMP, ESPECIALLY FOR OIL.

Publications (1)

Publication Number Publication Date
WO2004038224A1 true WO2004038224A1 (en) 2004-05-06

Family

ID=11440376

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IT2003/000658 WO2004038224A1 (en) 2002-10-23 2003-10-23 Variable-delivery rotary vane pump

Country Status (4)

Country Link
EP (1) EP1579117A1 (en)
AU (1) AU2003283809A1 (en)
IT (1) ITBO20020668A1 (en)
WO (1) WO2004038224A1 (en)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE403530A (en) *
NL287216A (en) *
GB331054A (en) * 1929-01-03 1930-07-03 Thomas Winter Nichols Improvements in rotary pumps, compressors and the like
US2510609A (en) * 1946-12-23 1950-06-06 William W Tingle Variable capacity hydraulic rotary pump or motor
US3511584A (en) * 1968-01-22 1970-05-12 Robert L Vierling Rotary fluid power devices
US4527968A (en) * 1983-03-04 1985-07-09 Mitsubishi Denki Kabushiki Kaisha Vane-type pump with rotatable casing therein driven from pump shaft
EP1225337A2 (en) * 2001-01-20 2002-07-24 Günther Beez Vane pump with capacity control

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE403530A (en) *
NL287216A (en) *
GB331054A (en) * 1929-01-03 1930-07-03 Thomas Winter Nichols Improvements in rotary pumps, compressors and the like
US2510609A (en) * 1946-12-23 1950-06-06 William W Tingle Variable capacity hydraulic rotary pump or motor
US3511584A (en) * 1968-01-22 1970-05-12 Robert L Vierling Rotary fluid power devices
US4527968A (en) * 1983-03-04 1985-07-09 Mitsubishi Denki Kabushiki Kaisha Vane-type pump with rotatable casing therein driven from pump shaft
EP1225337A2 (en) * 2001-01-20 2002-07-24 Günther Beez Vane pump with capacity control

Also Published As

Publication number Publication date
ITBO20020668A1 (en) 2004-04-24
EP1579117A1 (en) 2005-09-28
ITBO20020668A0 (en) 2002-10-23
AU2003283809A1 (en) 2004-05-13

Similar Documents

Publication Publication Date Title
CN101832264B (en) Oil pump rotor
US9765778B2 (en) Variable displacement rotary pump and displacement regulation method
JPH10169571A (en) Infinitely variable ring gear pump
EP1972785B1 (en) Check valve for a vacuum pump
JPS59134392A (en) Pump
EP2180186A1 (en) Rotor drive mechanism and pump device
JP2012132356A (en) Oil pump
KR970009955B1 (en) Twin roller pump
US8834140B2 (en) Leakage loss flow control and associated media flow delivery assembly
EP1845262A2 (en) Axial flow positive displacement worm pump
WO1990007631A1 (en) Rotary suction and discharge apparatus
WO2004038224A1 (en) Variable-delivery rotary vane pump
JP2008298026A (en) Variable displacement pump
JP4928567B2 (en) Car supply pump
EP0628726A2 (en) Variable delivery vane pump
JP2010265852A (en) Vane pump
GB2443089A (en) Split rotor variable output gerotor pump
RU139028U1 (en) ROTARY HYDRAULIC MACHINE
USRE26383E (en) Huber hydraulic torque motors
KR0144132B1 (en) Gerotor pumps
CN209083414U (en) Single cylinder diesel
CN101672275A (en) Swinging-bucket type rotor pump
CN114109810A (en) Electric pump
JPS60182378A (en) Rotor driving apparatus for single-axis eccentric screw pump
JPS61152980A (en) Discharge variable type gear pump

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LU MC NL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2003775790

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 2003775790

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: JP

WWW Wipo information: withdrawn in national office

Country of ref document: JP